Spring brake actuator with diaphragm retainer

ABSTRACT

A brake actuator assembly including a pressure plate presenting an opening, a push rod that is coupled to the pressure plate, a diaphragm that is coupled to the pressure plate, and a retainer that engages the push rod. The push rod has an outer surface and at least one protrusion extending outward from the outer surface. The retainer engages the protrusion such that at least a portion of the diaphragm is positioned between the pressure plate and the retainer.

CROSS-REFERENCE TO RELATED APPLICATIONS

This application claims priority to and is a Continuation of U.S. patentapplication Ser. No. 16/301,500, filed on Nov. 14, 2018 (issued as U.S.Pat. No. 10,889,280 on Jan. 12, 2021), which is a national stageapplication from International Patent Application PCT/US2016/033475,filed on May 20, 2016, each of which is incorporated herein by referencein its entirety.

BACKGROUND OF THE INVENTION 1. Field of the Invention

The present invention is directed generally to a pneumatic spring brakeactuator and, more specifically, to a spring brake actuator assemblyhaving a diaphragm retainer.

2. Description of Related Art

A pneumatic brake system for a large, heavy-duty vehicle, such as a bus,truck, semi-tractor, trailer, recreational vehicle, or constructionequipment, typically includes a brake shoe and drum assembly that isactuated by an actuator operated by the selective application ofcompressed air. A conventional pneumatic spring brake actuator has botha service brake actuator, which actuates the brakes under normal drivingconditions by the application of compressed air, and an emergency orspring brake actuator, which actuates the brakes when air pressure hasbeen released from a pressure chamber.

One common type of spring brake actuator includes a diaphragm thatdivides the actuator into a pressure chamber and a spring chamber. Thespring chamber contains a large force compression spring that iscompressed when the pressure chamber is pressurized and the emergency orparking brakes are not applied. When the pressure chamber isdepressurized, the spring expands to apply the emergency or parkingbrakes. A pressure plate is positioned between the diaphragm and thespring within the spring chamber. A push rod is coupled to the pressureplate and extends through a dividing wall separating the spring brakeactuator from the service brake actuator. In one configuration, thediaphragm sealingly engages the push rod and/or pressure plate to sealthe pressure chamber from the spring chamber so that the emergency orparking brakes may be disengaged. The diaphragm must remain in sealingengagement with the push rod and/or pressure plate to allow theemergency or parking brakes to be disengaged by pressurization of thepressure chamber.

When the emergency or parking brakes are disengaged, the pressurechamber increases in volume and the spring chamber decreases in volume,which results in a pressure increase in the spring chamber. The springchamber is typically vented to prevent it from becoming pressurized. Oneway of venting the spring chamber while preventing water andcontaminants from entering the spring chamber is to include a fluid flowpath between the spring chamber of the spring brake actuator and theservice brake pressure chamber through the push rod. In such anactuator, a valve assembly is placed in the push rod to regulate airflow between the spring chamber and the service brake pressure chamber.

BRIEF SUMMARY OF THE INVENTION

One embodiment of the invention disclosed herein is directed to a brakeactuator assembly including a pressure plate presenting an opening, apush rod that is coupled to the pressure plate, a diaphragm that iscoupled to the pressure plate, and a retainer that engages the push rod.The push rod has an outer surface and at least one protrusion extendingoutward from the outer surface. The retainer engages the protrusion suchthat at least a portion of the diaphragm is positioned between thepressure plate and the retainer. The retainer preferably ensures thatthe diaphragm remains coupled to the pressure plate in the event thatpressurized air exerts a force on a side of the diaphragm that isopposite the retainer. A portion of the diaphragm may be clamped betweenthe retainer and the pressure plate. The push rod preferablyfrictionally engages the pressure plate.

The brake actuator assembly also preferably includes a bearing that iscoupled to the push rod. The bearing preferably includes threads thatengage threads on an interior surface of the push rod. Preferably, thebrake actuator assembly is used in a spring brake actuator. The springbrake actuator may be part of a double diaphragm brake actuator alsoincluding a service brake actuator. A valve assembly with a one-way sealvalve is preferably coupled to an end of the push rod to allow air todischarge from a spring chamber as the spring brake actuator moves froman engaged to a disengaged position.

Additional aspects of the invention, together with the advantages andnovel features appurtenant thereto, will be set forth in part in thedescription which follows, and in part will become apparent to thoseskilled in the art upon examination of the following, or may be learnedfrom the practice of the invention. The objects and advantages of theinvention may be realized and attained by means of the instrumentalitiesand combinations particularly pointed out in the appended claims.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a cross-sectional view of a spring brake actuator inaccordance with the invention described herein;

FIG. 2 is an exploded, cross-sectional view of a bearing, a pressureplate, a diaphragm, a retainer, and a push rod of the spring brakeactuator of FIG. 1;

FIG. 3 is an assembled, cross-sectional view of the components shown inFIG. 2;

FIG. 4 is a detail view of a protrusion of the push rod that engages theretainer;

FIG. 5 is a detail view of one end of the push rod;

FIG. 6 is a detail view of the other end of the push rod;

FIG. 7 is a close-up view of the end of the push rod shown in FIG. 6;

FIG. 8 is a cross-sectional view of the retainer;

FIG. 9 is a perspective view of the bearing;

FIG. 10 is a cross-sectional view of the bearing; and

FIG. 11 is a cross-sectional view of a valve assembly of the springbrake actuator of FIG. 1.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENT

A spring brake actuator in accordance with at least one embodiment ofthe invention described herein is identified generally as 10 in FIG. 1.Spring brake actuator 10 may be part of a tandem-type pneumatic brakeactuator also including a service brake actuator (not shown); however,it is also within the scope of the invention for the spring brakeactuator 10 to be used on its own. As is known in the art, spring brakeactuator 10 is designed to apply the emergency or parking brakes of avehicle on which it is installed.

The spring brake actuator 10 includes a sealed spring brake housing 12having first and second end walls 14 a and 14 b and a side wall 14 cthat is joined with and extends between the end walls 14 a and 14 b. Thespring brake housing 12 is formed by an adapter housing 16 that iscoupled with a spring brake cover 18. The adapter housing 16 has aflange 22 that is clamped by a C-shaped rolled rim 24 of spring brakecover 18 to secure the spring brake cover 18 to the adapter housing 16.The adapter housing 16 has a flange 26 that is operable to receive aclamp (not shown) to clamp a service brake cover (not shown) to theadapter housing 16.

An elastomeric diaphragm 28 spans the interior of the spring brakehousing 12. Diaphragm 28 has a peripheral edge 30 that is sealinglyclamped between the flange 22 of adapter housing 16 and the rolled rim24 of spring brake cover 18. Another diaphragm (not shown) may beclamped between flange 26 and a flange (not shown) of a service brakecover (not shown) to divide a service brake housing (not shown).

Diaphragm 28 fluidly divides the spring brake housing 12 into a pressurechamber 32 and a spring chamber 34. As shown in FIG. 2, diaphragm 28extends from its peripheral edge 30 to an inner edge 36 that surroundsan opening 38 in the diaphragm 28. The pressure chamber 32 is fluidlyconnected to a source of pressurized air through a port 40 shown inFIG. 1. The spring chamber 34 is sealed to protect the componentstherein from direct exposure to the atmosphere and common environmentalcontaminants.

A pressure plate 42 is positioned in the spring chamber 34 adjacent tothe diaphragm 28. A large force compression spring 44 is placed betweenthe pressure plate 42 and the spring brake cover 18. As shown in FIG. 2,pressure plate 42 includes a central section 46 that is generally shapedlike a truncated cone and a flange 48 extending radially outward fromthe central section 46. An axial opening 50 extends through centralsection 46. An interior surface 52 of pressure plate 42 surroundsopening 50. At one end of pressure plate 42, the interior surface 52includes a countersink or angled section 54. A cylindrical section 56extends from the angled section 54 to an annular groove 58. Acylindrical section 60 having a slightly larger diameter thancylindrical section 56 extends from groove 58 to a bell shaped section62. Bell shaped section 62 extends to a generally planar surface 64 offlange 48.

Referring to FIG. 3, groove 58 receives inner edge 36 of diaphragm 28.Inner edge 36 extends radially outward from an adjacent cylindricalsection 66 of diaphragm 28. Inner edge 36 is shaped to generally fillgroove 58 to join diaphragm 28 to pressure plate 42 and seal betweendiaphragm 28 and pressure plate 42. The cylindrical section 60, bellshaped section 62 and planar surface 64 of flange 48 generally match thecontour of diaphragm 28 so that the pressure plate 42 and diaphragm 28closely abut each other as shown in FIG. 3.

As shown in FIG. 3, a hollow push rod 68 has a first end 70 that ispress fit within the opening 50 of pressure plate 42 and a second end 72that extends through an opening 74 (FIG. 1) in adapter housing 16. Thepush rod 68 has a side wall 76 with inner and outer surfaces 78 and 80,respectively, identified in FIG. 2. Inner surface 78 surrounds apassageway 81 through the push rod 68. An annular protrusion 82 extendsradially outward from outer surface 80 near first end 70. Protrusion 82extends continuously around the cylindrical outer surface 80; however,it is within the scope of the invention for the protrusion 82 to notextend continuously around the outer surface 80 and/or for there to bemultiple protrusions like 82 extending outward from the outer surface80.

Referring to FIG. 5, at the first end 70 of push rod 68, inner surface78 has a first section 84 having a greater internal diameter than asecond section 86 to form a reduced wall thickness portion of push rod68. Threads are formed in a portion of second section 86 adjacent firstsection 84. Outer surface 80 of push rod 68 has a first section 88extending from first end 70 just beyond the second section 86 of innersurface 78, a second section 90 extending from the first section 88 anda third section 92 extending from the second section 90 to the secondend 72. The first section 88 has a slightly smaller outer diameter thanthe second section 90, and the second section 90 has a slightly smallerouter diameter than the third section 92. Referring to FIGS. 6 and 7,inner surface 78 has a third section 94 extending from second section 86to second end 72. Third section 94 angles radially outward from secondsection 86 to second end 72 to form a reduced wall thickness portion ofpush rod 68. Threads are formed in a portion of second section 86adjacent third section 94.

Push rod 68 is pressed into pressure plate 42 so that the outer surface80 of push rod 68 frictionally engages the interior surface 52 (FIG. 2)of pressure plate 42 to join the push rod 68 and pressure plate 42. Pushrod 68 is also pressed through the opening 38 (FIG. 2) in diaphragm 28to compress the inner edge 36 and cylindrical section 66 of diaphragm 28between push rod 68 and pressure plate 42 as shown in FIG. 3. A seal ispreferably formed between diaphragm 28 and push rod 68 and betweendiaphragm 28 and pressure plate 42.

A retainer 96 engages the protrusion 82 of push rod 68 to assist insecuring diaphragm 28 to pressure plate 42 and push rod 68. Referring toFIG. 8, retainer 96 has a first side 98 and a second side 100. Firstside 98 includes four concentric annular depressions, one of which isidentified as 102, that assist in frictionally engaging diaphragm 28, asshown in FIG. 4, to prevent slippage between the retainer 96 anddiaphragm 28. A peripheral edge 104 of first side 98 is curved to matchthe curvature of diaphragm 28 and bell shaped section 62 of pressureplate 42, as shown in FIGS. 3 and 4. Retainer 96 presents a centralopening 106 that receives a portion of push rod 68. Referring to FIG. 8,opening 106 includes a first section 108 adjacent first side 98 and asecond section 110 adjacent second side 100. First section 108 has asmaller internal diameter than second section 110 to form an annularsurface 112 between the first section 108 and second section 110. Asshown in FIG. 4, protrusion 82 of push rod 68 engages the annularsurface 112 of retainer 96 to clamp retainer 96 between protrusion 82and diaphragm 28 and to clamp diaphragm 28 between retainer 96 andpressure plate 42. A portion of the diaphragm 28 is preferablycompressed between the retainer 96 and pressure plate 42, which may forma seal between the diaphragm 28 and pressure plate 42 and between thediaphragm 28 and retainer 96. In particular, retainer 96 prevents thediaphragm 28 from being forced away and decoupled from pressure plate 42if pressurized air enters the space between push rod 68 and pressureplate 42 and exerts a force on diaphragm 28 in a direction pushing thediaphragm 28 away from the pressure plate 42. Retainer 96 is generallyannular and extends laterally outward from the outer surface 80 of pushrod 68.

Referring to FIG. 9, a bearing 114 has a head 116 and a cylinder 118with a smaller outer diameter than head 116. Cylinder 118 has a threadedouter surface 120 that is positioned within push rod 68 and engages thethreaded second section 86 of push rod 68, as shown in FIG. 3, therebyjoining the bearing 114 to the push rod 68. The bearing 114 is alsoindirectly joined to the pressure plate 42, diaphragm 28 and retainer96. Referring to FIG. 10, bearing 114 includes a truncated conicalsurface 122 extending from head 116 to cylinder 118. The truncatedconical surface 122 mates with the angled section 54 of pressure plate42 shown in FIG. 2. As shown in FIG. 3, the first section 84 of push rod68 is swaged between the truncated conical surface 122 (FIG. 10) ofbearing 114 and the angled section 54 (FIG. 2) of pressure plate 42 toform a seal between the bearing 114, push rod 68, and pressure plate 42.Threading bearing 114 into push rod 68 may pull push rod 68 towardbearing 114 and generate a clamping force that clamps diaphragm 28between retainer 96 and pressure plate 42. It is within the scope of theinvention for the bearing 114 to be bonded to the push rod 68 inaddition to or instead of being joined with threads. For example, thebearing 114 can be welded to the push rod 68.

As shown in FIG. 10, bearing 114 has a smooth inner surface 124surrounding an opening 126. Grooves 128 a-b, shown in FIG. 9, are formedin head 116. Grooves 128 a-b preferably assist in allowing air to movefrom spring chamber 34 through opening 126 into the passageway 81 formedwithin push rod 68, particularly when bearing 114 is positioned adjacentspring brake cover 18 as shown in FIG. 1. Spring chamber 34 is in fluidcommunication with the passageway 81 within push rod 68 through theopening 126 in bearing 114.

The push rod 68 extends from its first end 70, which is positioned nearspring chamber 34, through a bearing and seal assembly 130 (FIG. 1)positioned within opening 74 formed in the adapter housing 16 to itssecond end 72, which may be positioned in a service brake pressurechamber (not shown). The bearing and seal assembly 130 is well known inthe art and thus is not described in more detail herein.

An opening 132 (FIG. 1) in spring brake cover 18 is aligned with opening126 (FIG. 9) in bearing 114 and opening 50 (FIG. 2) in pressure plate42. Referring to FIG. 1, a caging bolt assembly 134 includes anadjustment nut 136 threaded onto and permanently affixed to one end of acaging bolt 138, which terminates at its other end in a caging bolt head140. The caging bolt head 140 and a portion of the caging bolt 138extending from the head 140 are positioned within the passageway 81 ofthe push rod 68. The caging bolt 138 extends through the opening 126(FIG. 9) of the bearing 114 and through the opening 132 in the springbrake cover 18. The caging bolt 138 is threaded through a cap or collar142, which is riveted and permanently affixed to the spring brake cover18 in a substantially sealed manner so that air cannot pass throughopening 132.

The caging bolt head 140 preferably includes a bearing (not shown)positioned between opposing collars (not shown). The bearing (not shown)contacts the inner surface 78 (FIG. 2) of the push rod 68 to prevent thecollars (not shown) and caging bolt 138 from contacting the innersurface 78 while helping to guide the reciprocal movement of the pushrod 68 during the application and release of the emergency brakes. Axialslots (not shown) are formed in the face of the bearing (not shown) toform a fluid flow path around the bearing (not shown) so that the springchamber 34 is in fluid communication with the entire passageway 81within the push rod 68.

The caging bolt assembly 134 is operable to mechanically retract andhold the large force compression spring 44 in a compressed state (asshown in FIG. 1). By engaging the adjustment nut 136 with a wrench orsocket and rotating the nut 136 and caging bolt 138, the caging bolt 138moves to the left when viewed as shown in FIG. 1 until the majority ofthe caging bolt 138 is withdrawn from the spring brake housing 18. Asthe caging bolt 138 is withdrawn, the caging bolt head 140 contacts thebearing 114 to move the bearing 114, push rod 68, and pressure plate 42toward the end wall 14 a of the spring brake housing 18 therebycompressing the spring 44. Because the caging bolt head 140 has adiameter that is greater than the diameter of the opening 126 in bearing114, the caging bolt 138 is operable to couple the pressure plate 42 tothe spring brake cover 18 via the connection between the bearing 114 andpressure plate 42 and the connections between the caging bolt 138,collar 142, and spring brake cover 18. Caging the large forcecompression spring 44 in this manner, as shown in FIG. 1, is well knownand is typically utilized during assembly of the spring brake actuator10 and/or for the mechanical release of the emergency or parking brakesin the case of a failure or absence of the compressed air systemconnected to port 40. When the vehicle on which spring brake actuator 10is installed is in active use, the caging bolt 138 is moved to the rightwhen viewed as shown in FIG. 1 so that the spring 44, pressure plate 42,and push rod 68 may move freely with respect to the caging bolt 138.When the emergency or parking brakes are applied and retracted byexpansion and contraction of spring 44, surface 124 (FIG. 10) of bearing114 slides on the caging bolt 138 to guide and center the push rod 68,pressure plate 42, and diaphragm 28.

As shown in FIG. 1, a valve assembly 144 is joined to and closes thesecond end 72 of the push rod 68 for regulating fluid flow betweenspring chamber 34 and a service brake pressure chamber (not shown).Referring to FIG. 11, valve assembly 144 includes a valve body 146having a generally circular transfer plate 148 that is joined to acylindrical protrusion 150. The cylindrical protrusion 150 has athreaded side wall 152 that engages the threaded inner surface 78 ofpush rod 68 shown in FIG. 6. The protrusion 150 is at least partiallypositioned within the passageway 81 of the push rod 68. An o-ring seal154 is positioned at the base of protrusion 150 between the threadedside wall 152 of the valve assembly 150 and push rod 68 to prevent fluidfrom flowing between the side wall 152 of valve assembly 150 and pushrod 68. The third section 94 of the inner surface 78 of push rod 68,shown in FIG. 7, is configured to engage and squeeze seal 154 to preventfluid from flowing between side wall 152 of valve assembly 150 and pushrod 68 without damaging seal 154. Preferably, a liquid sealant isapplied to the threaded side wall 152 before the valve assembly 144 isthreaded within the push rod 68. The liquid sealant hardens to form aseal between the valve assembly 144 and push rod 68 and also preventsthe valve assembly 144 from becoming loose from the push rod 68. Thetransfer plate 148 is preferably sized to be received within a recess156 (FIG. 1) in the adapter housing 16.

A seal 158, spring 160, and retainer 162 are positioned inside a channel164 defined by an interior surface 166 of the valve body 146. Thetransfer plate 148 of the valve body 146 has first and second surfaces167 and 168 that are joined by a side wall 170. The cylindricalprotrusion 150 of the valve body 146 has first and second surfaces 172and 174 that are joined by threaded side wall 152. The second surface174 of the protrusion 150 is joined to and is integral with the firstsurface 167 of transfer plate 148. The channel 164 through valve body146 includes a first cylindrical section 176 extending from the firstsurface 172 of cylindrical protrusion 150, a second cylindrical section178 extending from first cylindrical section 176 to transfer plate 148,and a third cylindrical section 180 extending from second cylindricalsection 178 to second surface 168 of transfer plate 148. Secondcylindrical section 178 has a diameter that is greater than firstcylindrical section 176, and third cylindrical section 180 has adiameter that is greater than second cylindrical section 178. Thechannel 164 also includes a fourth section 182 extending throughtransfer plate 148 between openings 184 and 186 in side wall 170.

Seal 158 has a first section 188 with an outer diameter that is slightlyless than the diameter of first cylindrical section 176. Seal 158 has asecond section 190 that is integral with first section 188 and that hasan outer diameter that is slightly less than the diameter of secondcylindrical section 178. A square ring seal 192 is positioned within agroove around the base of the first section 188. An end of spring 160 ispositioned within an internal cavity 194 of seal 158 around a springretaining cylinder 196. The other end of spring 160 abuts retainer 162.Spring 160 biases seal 158 to a closed position, in which square ringseal 192 engages interior surface 166 of valve body 146 to prevent fluidfrom flowing through channel 164. Retainer 162 has a diameter that issubstantially equal to the diameter of third cylindrical section 180.Retainer 162 is pressed into third cylindrical section 180 to retainseal 158 and spring 160 within channel 164. Retainer 162 has openings,one of which is identified as 197, to allow air to flow through it. Afilter 198 is adhered to the first surface 172 of cylindrical protrusion150.

Seal 158 is moveable between the closed position shown in FIG. 11, inwhich fluid is blocked from flowing between the spring chamber 34(FIG. 1) and service brake pressure chamber (not shown) on the oppositeside of wall 14 b to an open position (not shown), in which fluid canflow between the spring chamber 34 and the service brake pressurechamber (not shown) through the channel 164 of the valve body 146. Inthe open position (not shown), seal 158 is moved to the left, whenviewed as shown in FIG. 11, and spring 160 is compressed. Seal 158 movesfrom its closed position to its open position when the pressure inspring chamber 34 increases to a threshold level at which the forceexerted on a surface 200 of seal 158 due to the pressure in springchamber 34 and passageway 81 is greater than the sum of the forcesexerted on the seal 158 due to the pressure in service brake pressurechamber (not shown) and the biasing force of spring 160. When the seal158 is in its closed position, service brake pressure chamber (notshown) can be pressurized to activate a service brake actuator (notshown) without undesirably pressurizing the spring chamber 34.

Valve assembly 144 is a one-way valve that allows air to vent from thespring chamber 34 as pressure chamber 32 is being pressurized and springchamber 34 is being compressed to deactivate a vehicle's emergency orparking brakes. Valve assembly 144 does not allow air into springchamber 34 to prevent formation of a vacuum in the spring chamber 34when the emergency or parking brakes are applied. Instead, spring 44 issized to overcome any vacuum formed in spring chamber 34 to timely applya vehicle's emergency or parking brakes.

In operation, the spring brake actuator 10 is moveable between thedisengaged position shown in FIG. 1 and an engaged position (not shown)as described herein. When the vehicle on which spring brake actuator 10is installed is parked for an extended period of time, the spring brakeactuator 10 is typically in the engaged position. In the engagedposition, pressure is released from the pressure chamber 32 so that thecompression spring 44 pushes the pressure plate 42 and the diaphragm 28toward the adapter housing 16. As a result, the push rod 68 connected tothe pressure plate 42 is pushed through the opening 74 in the adapterhousing 16. The transfer plate 148 (FIG. 11) of the valve assembly 144exerts a force on a diaphragm (not shown) and pressure plate (not shown)of a service brake actuator (not shown), which actuates the vehicle'sparking or emergency brakes. When the spring brake actuator 10 is in theengaged position, the vehicle on which the spring brake actuator 10 isinstalled cannot move. To allow the vehicle to move, the spring 44 mustbe retracted either by pressurizing the pressure chamber 32 or bymechanically retracting the spring 44 with caging bolt 138, as shown inFIG. 1 and described above. Mechanical retraction of spring 44 withcaging bolt 138 is typically only necessary during assembly of thespring brake actuator 10 and/or when mechanical release of the springbrake actuator 10 is necessary due to a failure or absence of thecompressed air system connected to port 40.

When pressure chamber 32 is pressurized, diaphragm 28 and pressure plate42 retract spring 44 and compress it against housing wall 14 a to movethe spring brake actuator 10 to its disengaged position. The movement ofpressure plate 42 causes push rod 68 to retract through opening 74 inadapter housing 16, which releases the vehicle's parking brakes. Bearing114 allows the pressure plate 42 and push rod 68 to move with respect tothe caging bolt 138 between the engaged and disengaged positions whilepreventing damage to the pressure plate 42, push rod 68, and caging bolt138. The inner surface 124 (FIG. 10) of the bearing 114 is in closecontact with caging bolt 138 to guide movement of the pressure plate 42and push rod 68. The inner surface 124 of the bearing 114 is preferablyrelatively smooth to minimize damage to the threads of the caging bolt138.

As pressure chamber 32 is pressurized to release the vehicle's parkingbrakes, the volume of the pressure chamber 32 increases due to theretraction of spring 44. As the volume of pressure chamber 32 increases,the volume of spring chamber 34 decreases thereby increasing thepressure of the air contained therein. The pressurized air in the springchamber 34 is fluidly connected to the valve assembly 144 through thebearing 114 and the passageway 81 through the push rod 68. Thepressurized air entering valve assembly 144 exerts a force on seal 158(FIG. 11) that moves seal 158 to its open position when the biasingforce of spring 160 is overcome. The pressurized air flows through valveassembly 144 into a service brake pressure chamber (not shown) toprevent pressure build up in spring chamber 34. Spring 160 moves seal158 back to its closed position when the sum of the biasing force ofspring 160 and force exerted on seal 158 due to pressure in the servicebrake pressure chamber (not shown) is greater than the force exerted onseal 158 by the pressurized air in spring chamber 34.

When the spring brake actuator 10 is applied by exhausting thepressurized air from pressure chamber 32, the volume of spring chamber34 expands causing the pressure within the chamber 34 to drop. As valveassembly 144 is a one-way valve that is biased to a closed position, airdoes not flow through the valve assembly 144 from the service brakepressure chamber (not shown) into the spring chamber 34 to alleviate thevacuum. However, spring 44 is sized to overcome any vacuum formation inspring chamber 34 so that the emergency brakes are timely applied.

When the spring brake actuator 10 is in the disengaged position shown inFIG. 1 and the vehicle on which the brake actuator 10 is installed is intransit, a service brake actuator (not shown) is utilized to brake thevehicle. Valve assembly 144 is biased to a closed position to preventair from the service brake actuator (not shown) from entering springchamber 34 through valve assembly 144.

From the foregoing it will be seen that this invention is one welladapted to attain all ends and objectives herein-above set forth,together with the other advantages which are obvious and which areinherent to the invention.

Since many possible embodiments may be made of the invention withoutdeparting from the scope thereof, it is to be understood that allmatters herein set forth or shown in the accompanying drawings are to beinterpreted as illustrative, and not in a limiting sense.

While specific embodiments have been shown and discussed, variousmodifications may of course be made, and the invention is not limited tothe specific forms or arrangement of parts and steps described herein,except insofar as such limitations are included in the following claims.Further, it will be understood that certain features and subcombinationsare of utility and may be employed without reference to other featuresand subcombinations. This is contemplated by and is within the scope ofthe claims.

What is claimed and desired to be secured by Letters Patent is asfollows:
 1. A brake actuator assembly comprising: a pressure platepresenting an opening; a push rod that is coupled to the pressure plate,wherein the push rod comprises an outer surface and at least oneprotrusion extending outward from the outer surface; a diaphragm that iscoupled to the pressure plate; and a retainer that engages theprotrusion, wherein at least a portion of the diaphragm is positionedbetween the pressure plate and the retainer.
 2. The brake actuatorassembly of claim 1, wherein the push rod is at least partially receivedby the opening.
 3. The brake actuator assembly of claim 2, wherein thepush rod frictionally engages an interior surface of the pressure platesurrounding the opening.
 4. The brake actuator assembly of claim 1,wherein a portion of the diaphragm is positioned between the pressureplate and the push rod.
 5. The brake actuator assembly of claim 1,wherein the protrusion is annular.
 6. The brake actuator assembly ofclaim 1, wherein the retainer is annular and extends laterally outwardfrom the push rod.
 7. The brake actuator assembly of claim 1, wherein aportion of the diaphragm is compressed between the retainer and thepressure plate.
 8. The brake actuator assembly of claim 1, wherein aninterior surface of the pressure plate surrounds the opening, andwherein a groove formed in the interior surface receives an end of thediaphragm.
 9. The brake actuator assembly of claim 1, wherein at least aportion of the retainer is positioned between the protrusion and thediaphragm.
 10. The brake actuator assembly of claim 1, wherein a bearingis coupled to the push rod, and wherein at least a portion of thebearing is received within the push rod.
 11. The brake actuator assemblyof claim 10, wherein the bearing comprises threads that engage threadsformed in the push rod.
 12. The brake actuator assembly of claim 10,wherein an end of the push rod is swaged between the bearing and thepressure plate.
 13. The brake actuator assembly of claim 1, wherein thepush rod comprises an interior surface surrounding a passageway, andfurther comprising a valve assembly that is coupled to the push rod. 14.The brake actuator assembly of claim 13, further comprising a housingthat is divided by the diaphragm into a spring chamber and a pressurechamber, wherein the valve assembly comprises a seal that is biased to aclosed position with a biasing force, and wherein the seal is operableto move to an open position when a force exerted on the seal due to apressure in the spring chamber exceeds the biasing force.
 15. The brakeactuator assembly of claim 14, wherein the valve assembly is operable toexhaust air from the spring chamber and the passageway when the seal isin the open position, and wherein the valve assembly blocks air fromentering the spring chamber through the passageway when the seal is inthe closed position.